Automatic vise jaw

ABSTRACT

An automatic vise jaw wherein a movable jaw is urged toward a fixed vise jaw by means of crank operated screw. The movable jaw is equipped with integral air cylinders to actuate a pressure plate for work holding purposes. The air cylinders function piston rods which operatively cooperate with the pressure plate by means of linkage interposed therebetween. By employing suitable leverage, the linkage serves to substantially increase the ratio of pressure applied at the air cylinders and to rapidly apply the increased pressure at the pressure plate.

United States Patent [1 1 Newswanger Sept. 11, 1973 AUTOMATIC VISE JAW[76] Inventor: Paul S. Newswanger, 1401 Vermont Ave., Lancaster, Pa.

[22] Filed: June 25, 1971 [2!] Appl. No.: 158,550

[52] U.S.-CI 269/27, 269/32, 269/229 [51] Int.'Cl B25b l/08, B25b H18[58] Field of Search 269/27, 28, 32, 228,

[56] References Cited UNITED STATES PATENTS 7/1959 Alexander 269/32 X2,443,775 6/1948 Olson 269/32 FOREIGN PATENTS OR APPLICATIONS 9/1960Great Britain 269/27 Primary Examiner-Harold D. Whitehead AssistantExaminerE. F. Desmond Att0r ney'Karl L. Spivak et al.

571 ABSTRACT An automatic vise jaw wherein a movable jaw is urged towarda fixed vise jaw by meansof crank operated screw. The movable jaw isequipped with integral air cylinders to actuate a pressure plate forwork holding purposes. The air cylinders function piston rods whichoperatively cooperate with the pressure plate by means of linkageinterposed therebetween. By employing suitable leverage, the linkageserves to substantially increase the ratio of pressure applied at theair cylinders and to rapidly apply the increased pressure at thepressure plate.

9 Claims, 13 Drawing Figures 1 AUTOMATIC VlSE JAW BACKGROUND OF THEINVENTION The present invention relates generally to the field ofmachine tools, and more particularly, is directed to an automatic visejaw for use in holding various work pieces for machining operations.

It is the common practice to employ work holding vises in conjunctionwith conventional machine tools such as drill presses, milling machines,grinders and similar metal working machinery- Most conventional visesinclude a stationary jaw and a movable jaw, the movable jaw beingmovable with respect to the fixed jaw by means of a crank and screw. Byplacing a work piece between the fixed and movable jaws and then turningthe crank, a work piece could be tightly gripped for the machiningoperations.

The prior art vises of which I am familiar are relatively slow inoperation in that the machine operator must manually turn the crankuntil sufficient pressures are built up to securely hold the work piecebetween the fixed and movable jaws. In thos instances wherein it isdesired to machine a great number of pieces in a production run, thelength of time required to alternately tighten and loosen work pieces inthe vise by means of the hand operated crank greatly slows down themachining operations and thereby increases the final cost of the itemsso treated. Additionally, the pressure generated to tighten the workpiece within the vise jaws was directly proportional to the pressureexerted by the machine operator on the crank handle. In order to tightenand loosen a number of pieces during a production run, considerablemanual effort on the part of the operator was required. Accordingly,fatigue of the operator is an important consideration in productionoperation. The exertions required to alternately tighten and loosen thejaw vise manually by tightening and loosening the crank handle requiresconsiderable exertion on the part of the operator and could result innoticeable slow down by the end of a busy day.

Prior workers in the art have attempted to introduce the advantages ofhydraulic pressure in conjunction with vises to both speed up and toincrease the available pressure for holding work pieces. For example, adevice is disclosed in U.S. Pat. No. 2,803,157 which employs a screwthread and hydraulic pressure for exerting forces against a work piece.A hollow spindle is employed which is turned by a ratchet bolt todisplace a spring pressed pawl. Another prior art device employs a powerplunger which incorporates a lever and has a renewable bearing memberfor direct contact with the plunger as set forth in U.S. Pat. No.2,052,976.

ln U.S. Pat. No. 2,656,820,a power operated vise includes a fixed jawand amovable jaw which is movable by a screw in conventional manner. Apiston axially aligns with the screw and employs a threaded sleeve nut.All of the prior art automatic vise jaws of which I am aware incorporatemeans to operate a movable jaw but are not equipped with linkage meansto rapidly exert greatly multiplied forces upona pressure plate tothereby allow rapid interchangeability of work pieces during productionruns. Additionally, the prior art devices are relatively complicated innature and in construction are not compatible for use with existingequipment.

' SUMMARY OF THE INVENTION The present invention relates to the field ofautomaticvise jaws, and more particularly, is directed to a cylinderoperated movable jaw :for rapidly exerting greatly multiplied forcesupon a work piece.

The present invention is compatible with most vises presently utilizedon existing equipment, such as those manufactured by Bridgeport MachineTool Company. The fixed jaw construction and the usual vise screw areemployed in well known manner and are re-used with the presentinvention. The movable jaw. may be removed from the existing vise andreplaced 'by a jaw which has been machined to accommodate two aircylinders for jaw actuation by air pressure. An axially aligned path isprovided for each air cylinder piston actuated plunger which rapidlyreciprocates forwardly for work holding purposes and rearwardly for workreleasing. The plungers contact linkage which is suitably pivoted withinthe movable jaw construction to exert an increased ratio of pressureupon a work contacting pressure plate. The pressure plate forwardlyconnects to the movable jaw and in conjunction with the vise fixed jawforms the work holding components. Activation of the air cylinders urgesthe plungers forwardly into contact with the operating linkage. Thelinkage in turn presses against the pressure plate to urge the pressureplate toward the fixed jaw for work holding purposes. By judiciouslyconstructing the linkage to increase the pressure ratio, great pressurescan be quickly and easily built up at the pressure plate to securelyhold a work piece during any machining operation.

The operator can turn the conventional screw of the vise to move themovable jaw until the work piece is loosely held. Optimumly, the part tobe machined is a free sliding fit between the fixed jaw and the pressureplate with a clearance of approximately one-sixtyfourth of an inchtherebetween. Energization of the air cylinders causes the plungers toactivate the linkage which forwardly press the pressure plate tosecurely hold the work piece between the fixed jaw and the pressureplate. Enormous pressures can be applied quickly and easily to the workpiece by the leverage obtained at the operating linkage. After themaching operation is performed, the air switch is opened to rapidlyreduce the pressure holding the work piece, thereby allowing the'workpiece to be easily removed from between the pressure plate and the fixedjaw without requiring any manual adjustment of the vise screw.

It should be noted that once the pressure plate is properly located bythe screw of the vise for a production run of similar parts, the screwneed not again be It is another object of the present invention to pro-.

vide a novel automatic vise jaw that incorporates existing visecomponents such as the base, the fixed jaw and the screw.

.It is another object of the present invention to provide a novelautomatic vise jaw that includes a pressure plate affixed to the movablevise jaw for work clamping purposes.

It is another object of the present invention to provide a novelautomatic vise jaw wherein an air cylinder is employed with suitablelinkage to increase the ratio of pressure available for work clampingpurposes.

It is another object of the present invention to provide a novelautomatic vise jaw that incorporates an air operated plunger whichfunctions operating linkage to energize a work holding pressure plate.

It is another object of the present invention to provide a novelautomatic vise jaw equipped with a pressure plate operable forwardly ofthe jaw and being activated by air cylinder operated linkage to increasethe working pressure.

It is another object of the present invention while having all the aboveimprovements and features, to incorporate safety features insuring theoperators safety. Because of the small amount of travel by the pressureplate forwardly from the moving jaw, a maximum travel of approximatelyone sixteenth of one inch makes it almost impossible for the operator tohave his fingers caught and pinched.

It is another object of the present invention to provide a novelautomatic vise jaw including a forwardly positioned pressure plate, thepressure plate being pivotal with respect to the jaw construction forwork piece clamping purposes.

It is another object of the present invention to provide a novelautomatic vise jaw that is compatible for use with existing machine toolwork holding vises.

It is another object of the present invention to provide a novelautomatic vise jaw that is inexpensive in manufacture, rugged inconstruction and trouble-free when in use.

Other objects and a fuller understanding of the invention will be had byreferring to the following description and claims of a preferredembodiment thereof, taken in conjunction with the accompanying drawingswherein like reference characters refer to similar parts throughout theseveral views and in which:

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a side elevational view of avise assembly incorporating the present invention.

FIG. 2 is an enlarged,. cross sectional view taken along Line 2-2 ofFIG. 1, looking in the direction of the arrows.

FIG. 3 is a cross sectional view taken along Line 33 of FIG. 2, lookingin the direction of the arrows.

FIG. 4 is an enlarged, cross sectional view taken along Line 4-4 of FIG.2, looking in the direction of the arrows, showing the pressure plate ininitial position.

FIG. 5 is a view similar to FIG. 4, but showing the parts in workclamping position.

FIG. 6 is an end elevational view on reduced scale, taken along Line 6-6of FIG. 4, looking in the direction of the arrows.

FIG. 7 is a partial, cross sectional view taken along Line 7-7 of FIG.6, looking in the direction of the arrows.

FIG. 8 is a sectional view taken along Line 8-8 of FIG. 3, looking inthe direction of the arrows.

FIG. 9 is a diagrammatic view similar to FIG. 4, showing a modifiedplunger and linkage arrangement.

FIG. 10 is a diagrammatic view similar to FIG. 4, showing a secondmodified plunger and linkage arrangement.

FIG. 11 is a sectional view similar to FIG. 2, showing a modifiedlinkage arrangement.

FIG. 12 is a cross sectional view taken along Line 12-12 of FIG. 11,looking in the direction of the arrows, showing the pressure plate ininitial position.

FIG. 13 is a view similar to FIG. 12 showing the parts in work clampingposition.

DESCRIPTION OF THE PREFERRED EMBODIMENTS OF THE INVENTION Althoughspecific terms are used in the following description for the sake ofclarity, these terms are intended to refer only to the particularstructure of my invention selected for illustation in the drawings andare not intended to define or limit the scope of the invention.

Referring now to the drawings, I show in FIG. 1 a machine vise 10 whichincludes a stationary base 12 which is adaptable to be mounted upon thetable 14 of a conventional machine tool such as a milling machine or adrill press (not shown). The stationary base 12 conventionally mountsupon the table 14 by utilizing mounting bolts 16 or other suitablefastening means in well known manner. The stationary base 12 forwardlysupports the fixed vise jaw 18 and terminates rearwardly in a verticalflange 20 in the usual manner. The vertical flange 20 is provided withan internal screw thread which threadedly receives the vise screw 22 inconventional, threaded engagement therein. The vise screw 22 terminatesrearwardly in a crank handle 24 and forwardly engages the movable visejaw 26. Thus, by rotating the crank handle 24 to turn the vise screw 22within the threaded connection in the vertical flange 20, the movablejaw 26 may be moved forwardly or rearwardly in conventional manner tothereby vary the spacing between the pressure plate 28 of the movablejaw 26 and the fixed plate 30 of the fixed vise jaw 18.

As best seen in FIGS. 2, 3 and 8, the movable vise jaw 26 is drilled orotherwise treated to provide a pair of spaced, longitudinally extendingair cylinders 32, 34. Pistons 36, 38 respectively reciprocate within theair cylinders 32, 34 to longitudinally reciprocate their associatedpiston rods 40, 42. An air intake line 44 is conventionally energized byan air hose 46 and simultaneously introduces air under pressure intoeach air cylinder 32, 34 intermediate the heads of the pistons 36, 38and the air cylinder seals 48, 50. Energization of the air intake line44 introduces line air pressure upon the heads of the pistons 36, 38 toforwardly urge the pistons 36, 38 and the affixed piston rods 40, 42.Return springs 52, 54 bias between the forward ends of the air cylinders32, 34 and the forward faces of the pistons 36, 38 to urge the pistons36, 38 to return to their initial position once air pressure from theair intake line 44 has been interrupted such as by means of an air valve56. Air bleed lines 58 communicate with the air cylinders 33, 34 tobleed air from within the air cylinders 32, 34 in conventional manner tofacilitate operation of the pistons 36, 38 upon energization of the airintake line As best seen in FIGS. 2, 4 and 5, the forward ends 60, 62 ofthe respective piston rods 40, 42 contact the power cams 64, 66 to pivotthe power earns 64, 66 in a counter clockwise direction about the jawaffixed pivot pins 68, 70. The cam surfaces 72, 74 of thepower cams 64,66 ride upon the cooperating cam surfaces 76, 78 of the jaw cams 80, 82to cause the jaw earns 80, 82 to rotate in a clockwise direction abouttheir respective movable jaw affixed pivot pins 84, 86. It will beobserved that the jaw cams 80, 82 are machined to provide a crank arm 88which swings from an angular position as in FIG. 4 when the aircylinders 32, 34 are deenergized to a generally horizontal position asin FIG. 5 when the air cylinders 32, 34 are activated. The forwardmostnose 90 of the crank arms 88 continuously contacts the rear surface ofthe pressure plate 28 during all periods of operation. When the aircylinders 32, 34 are de-activated and the jaw cams 80, 82 are disposedwith the crank arms 88 in angular relation as in FIG. 4, the distancebetween the respective pivot pins 84, 86 and the forwardmost nose 90 isforeshortened to permit the upper portion of the pressure plate 28 toabut the face 92 of the movable vise jaw 26. When the power cams arerotated by activation of the air cylinders 32, 34 to clockwise rotatethe jaw earns 80, 82 about their respective pivot pins 84, 86, the crankarms 88 dispose horizontally to increase the horizontal distance betweenthe pivot pins 84, 86 and the noses 90 of the jaw cams 80, 82. Thisincrease in horizontal distance of the noses 90 from the pivot pins 84,86 exerts great pressure upon the upper portion of the pressure plate 28to urge it forwardly from the face 92 of the movable vise jaw26. It hasbeen found that a forwardly urged movement of the upper portion of thepressure plate 28 of approximately one-sixteenth of an inch issufficient to exert great holding forces upon a work piece 94 to secureit between the pressure plate 28 and the fixed plate 30 of the fixedvise jaw 18.

As best'observed in FIGS. 6 and 7, the pressure plate 28 pivotallyconnects to the movable vise jaw 26 by employing a plurality of bottomlypositioned ball and socket junctions 96. A plurality of connectors 98each threadedly engage into the bottom of the movable vise jaw 26 andterminate forwardly in a ball head 100 which is preferably integrallyformed with the threaded shank portions 102 of the connectors 98. Thepressure plate 28 is drilled or otherwise machined to provide aplurality of circular sockets 104 of dimensions suitable to receive theball heads 100 in a ball and socket joint. Thus, when the air cylinders32, 34 are activated to forwardly push the piston rods 40, 42 which inturn rotate the power cams 64, 66 and the jaw earns 80, 82', themovement of the crank arms 88 to the horizontal position of FIG. 5serves to pivot the top of the pressure plate 28 outwardly byswivelling'the bottom of the pres- I sure plate about the ball andsocket junctions96. A pair of return coil springs 106, 108 have theirends respectively pinned to the upper portion of the pressure plate 28and to the interior of the movable vise jaw 26 in a manner tocontinuously bias the upper portion of the pressure plate against theface .92 of the movable vise jaw 26. Accordingly, after the aircylinders 32, 34 are energized and de-energized, the return coil springs106, 108 serve to return the pressure plate 28 to the unloaded initialposition as illustrated in FIG. 4.

Referring now to FIG. 9, I show a first modified jaw piston rod 40 whichis reciprocal within the movable vise jaw body 26 in the mannerhereinbefore described. The modified piston rod 40' terminates forwardlyin a 7 power ram 110 which has its forward action arm 112 in contactwith the bottom end of the jaw cam 80 in a manner to pivot the cam aboutits movable jaw affixed pivot pin 84 when the ram 110 is forwardly urgedby the piston rod 40'. Clockwise rotation of the jaw cam 80 about itspivot pin 84 causes the crank arm 88 to rotate to a generally horizontalposition whereby the nose 90 rides against the upper portion of thepressure plate 28 to force it outwardly away from the face 92 of themovable jaw 26 in the manner hereinbefore described. De-energization ofthe air cylinders 32, 34 will cause the piston rod 40' to reciprocaterearwardly, pulling the rod affixed power ram 110* also rearwardly tothereby permit the jaw cam 80 to rotate counterclockwise about its pivotpin 84. The return coil springs 106, 108 (not illustrated in FIG. 9)will then pull the upper portion of the pressure plate 28 against theface 92 of the movable vise jaw so that the pressure plate 28 camoperating mechanism which includes a modified is vertically disposed inunloaded position in the manner hereinbefore illustrated. By varying theleverage distance between the pivot pin 84 and the contact area withthe-forward action arm 112, the power multiplication available at thepressure plate 28 can be readily designed. 4 y

In a second modification, the piston rod 40 may be employed directlyagainst the interior cam face 114 of the jaw cam to urge it in clockwiserotation about the jaw cam pivot pin 84 to thereby rotate the crank arm88 into a generally horizontal position as illustrated. The cam nose 90will co-act with the upper portion of the pressure plate 28 in themanner hereinbefore described to pivot the pressure plate 28 about itsas in FIG. 9 is greater than the distance between the pivot pin 84 andthe point of contact 116 between the end of the piston rod 40 and theinterior cam face 114 as in FIG. 10. Accordingly, because of the greaterleverage available, a greater pressure can be imposed upon the pressureplate 28 by the construction illustrated in FIG. 9. By varying thedistance between the point of application of pressure upon the jaw cam80 and the pivot pin 84, the available pressure for work holdingpurposes may be readily controlled in accordance with usual power crankand arm calculations.

By employing the constructions illustrated in FIGS. 2, 9 or 10, greatpressures may be made available at the pressure plate 28 for workholding purposes. For example, by providing air cylinders 32, 34 of oneand onehalf inches in diameter, each piston 36, 38 will have a face area"of 1.767 square inches or a total of, 3,53

square inches. Applying air pressure at the air intake line 44 of forexample, one hundred pounds per square inch will generate a force ofthree hundred and fiftythree pounds per square inch in the cylinders 32,34.

Should the leverage ratio between the power cams 64, 66 and jaw cams80,82 as in FIG. 2, or between the power ram and the jaw cam 80 as in FIG.9 or the the line air pressure, the size of the cylinders or theleverage ratio between the operating parts, the available pressure atthe pressure plate 28 may be widely varied within desired limits toproduce any required work holding pressure.

It will be appreciated that the pressure plate 28 pivots near its bottomabout the ball and socket junctions 96 and it is therefore the tendencyof the pressure plate 28 to force a work piece 94 downwardly towards thebottom of the vise construction. The pivotal arrangement completelyeliminates any tendency of the applied pressure to squeeze the workupwardly between the pressure plate 28 and the fixed plate 30 andtherefore,

, an extremely reliable, work clamping arrangement can be provided.

Referring now to FIGS. 11, 12 and 13, I show a third modifiedconstruction which may be employed to function the pressure plate 28 ina vertical plane for clamping a work piece 94. In this embodiment, themovable vise jaw 26 is equipped with air cylinders, air intake lines,air cylinder seals, pistons and return springs in the mannerhereinbefore fully described for the embodiment illustrated in FIG. 2.The pistons (not shown) function modified piston rods 118, 120 whichreciprocate within the movable vise jaw body in response to activationof the air cylinders in the manner hereinbefore described. The pistonrods 118, 120 forwardly carry angular cam operators 122, 124 which eachterminate forwardly in a relatively narrow nose 126 and rearwardly in awidened shoulder 128. The movable vise jaw body is forwardly machined toprovide a pair of right and left operating cavities 130, 132 ofnecessary size to receive the upper and lower pressure plate operatinglinkage 134, 136, 138 and 140 therein for pressure plate operatingpurposes. The rearwardly positioned upper link arms 136 rearwardlypivotally connect to the movable vise jaw 26 about the upper pivot pins142. The forward upper link arms 134 forwardly pivotally connect to thepressure plate 28 at the forward pivot pins 144. Similarly, the lowerlinkage arms 140 rearwardly connect to the movable vise jaw 26 throughthe lower pivot pins 146 and the lower forward linkage arms 138forwardly pivotally affix to the pressure plate 28 at the lower pivotalconnections 148. The upper linkage arms 134, 136 pivotally respectivelyinterconnect at the pivot pins 150 which also carries the upper camfollower 152. Similarly, the lower linkage arms 138, 140 mediallypivotally interconnect at the contact with the forward face 92 of themovable vise jaw 26. See FIG. 12. It will be noted that the upper andlower linkage arms 134, 136, 138, 140 are fabricated of substantiallyidentical size. As best seen in,FIG. 12, the combined length of theupper linkage arms 134, 136 is greater than the distance between theupper pivot pin 142 and the pivotal connection 144 when the pressureplate 28 contacts the vise jaw forward face 92. Similarly, the lowerlinkage arms 138, 140 are fabricated to a combined length that isgreater than the distance between the lower pivot pin 146 and the lowerpivotal connection 148 when the pressure plate 28 connects the forwardface 92. The upper and lower linkage arms 134, 136 and 138, 140 thusserve as crank arms and are arranged with the respective upper and lowerpivot pins 150, 154 in close proximity so that the upper cam follower152 and the lower cam follower 156 are urged toward each other. Thepiston rod cam operators 122, 124 align between the respective upper andlower cam followers 152, 156 in a manner to force the noses 126 betweenthe upper and lower cam followers 152, 156 when the piston rods 118, areforwardly urged by activation of the air cylinders 32, 34.

As best seen in FIG. 13, activation of the air cylinders 32, 34 urgesthe piston rods 118, 120 forwardly within the respective operatingcavities 130, 132 to force the respective noses 126 of the cam operators122, 124 between the upper and lower cam followers 152, 156. Continuedforward movement of the piston rods 118, 120 causes the cam followers152, 156 to respectively ride up the inclined widened surfaces of thecam operators 122, 124 toward the widened shoulders 128. The movement ofthe cam operators 122, 124 forwardly with respect to the cam followers152, 156 causes the cam followers 152, 156 to separate and to tend toincrease the distance between the upper and lower movable vise jawaffixed pivot pins 142, 146 and the respective upper and lower pivotalconnections 144, 148 to the pressure plate 28 to thereby force thepressure plate 28 forwardly with respect to the forward face 92 of themovable vise jaw 26 for work piece 94 securing purposes. The pressureplate 28 will continue to exert pressure forces against the work piece94 as long as the air cylinders 32, 34 are activated to therebycontinuously urge the respectivepiston rods 118, 120 to the forwardposition as in FIG. 13. De-energization of the air cylinders 32, 34 willcause the piston rods 118, 120 to be pulled rearwardly by the returnsprings 52, 54 in the manner hereinbefore described to withdraw the camoperators 122, 124 from contact with the upper and lower cam followers152, 154 respectively. With the piston rods 118, 120 pulled to theirrearward position, the plurality of comer positioned springs 158 pullthe pressure plate 28 into vertical contact with the forward face 92 ofthe movable jaw 26 as in FIG. 12. Thus, the upper and lower linkage arms134, 136, 138, 140, the cam followers 152, 156 and the cam operators122, 124 all cooperate to function the pressure plate 28 forwardly andrearwardly in continuous vertical alignment.

In order to operate the device, the screw 22 of the vise is turned bymeans of the crank handle 24 until the work piece 94 is a sliding fitbetween the pressure plate 28-which is affixed to the movable jaw 26 andthe fixed plate 30 which connects to the fixed vise jaw 18. Optimumly,the distance between the pressure plate 28 and the fixed plate 30 isapproximately one sixty-fourth of an inch greater than the width of thework piece 94 to be machined. The work piece 94 is then placed betweenthe vise jaws 18, 26 in position for the desired machining operation.The air valve 56 which is of conventional construction of suitabledesign to control the air intake hose line 46 is then pivoted toenergize the air intake line 44 and the air cylinders 32, 34. Activationof the air cylinders 32, 34 causes the pressure plate 28 to pressagainst the work piece 94 with great pressure due to the leverage actionin the manner hereinbefore described in detail to permit the work pieceto be firmly held during the machining operations. After completion ofthe machining operations, the air valve 56 is closed, therebyde-activating the air cylinders 32, 34. This retracts the pressure plate28 to thereby allow the work piece 94 to be readily lifted clear frombetween the vise jaws 18, 26. Because of the rapid action of the aircylinders 32, 34 in response to operation of the air valve 56,considerable time may be saved in securing and removing work pieces frombetween the jaws of a vise as compared to the former method of turningthe crank handle 24 for work tightening and loosening purposes for eachwork piece thus treated. It will be noted that by employing the air visejaw of the present invention, once the screw 22 has been turned toproperly position the jaws for a given size work piece, production runsof similar pieces may be made without again turning the crank handle 24.The movable pressure plate 28 and its air activated operating mechanismcooperate for work securing purposes.

I claim:

1. In an automatic operating vise of the type incorporating a fixed jawand an adjustable jaw movable with respect to the fixed jaw to secure awork piece therebetween, the combination of A. cylinder means providedin one said jaw,

1. said cylinder means having a piston reciprocal therein,

2. said cylinder means receiving activating forces to pushthe pistonfrom a first position to a second position within the cylinder means,

a. said piston moving a piston rod within the said jaw in response tothe activating forces,

b. said cylinder means including means to return the piston to its saidfirst position upon removal of the activating forces;

B. linkage means in contact with the said piston rod,

1. said linkage means having an initial position when the said cylinderis de-activated and having a pressure position when the activatingforces push the piston to its said second position; and

C. pressure plate means connected to one said vise jaw,

1. said pressure plate means having an initial position in overallcontact with its associated vise jaw when the cylinder means isde-activated and being urged to a pressure position by the activatingforces,

a. said linkage means pushing at least a portion of the pressure platemeans out of contact with its associated vise jaw when the piston ispushed to its said second position,

2. the said pressure plate means being connected to the one said visejaw by means of ball and socket junctions.

2. The invention of claim 1 wherein theballand socket junctions permitpivotal movement of the pres-- sure plate means with regard to theassociated vise jaw.

3. In an automatic vise of the type incorporating a fixed jaw and anadjustable jaw movable with respect to the fixed jaw to secureaworkpiece therebetween,

the combination of A. cylinder'means provided in one said jaw,

1. said cylinder means having a piston reciprocal therein, 2. saidcylinder means receiving activating forces to push the piston from afirst position to a second position within the cylinder means,

a. said piston moving a piston rod within the said jaw in response tothe activating forces,

b. said cylinder means including means to return the piston to its saidfirst position upon removal of the activating forces,

3. the one said jaw being the adjustable jaw;

B. linkage means in contact with the said piston rod,

1. said linkage means having an initial position when the said cylinderis de-activated and having a pressure position when the activatingforces push the piston to its said second position,

2. said linkage means comprising a power cam and a jaw cam pivotallyconnected to the adjustable ja a. the said piston rod pivoting the powercam upon function of the cylinder means and the said power cam pivotingthe jaw cam to urge the pressure plate means outwardly from theadjustable jaw; and

C. pressure plate means connected to one said vise i. said pressureplate means having an initial posi tion in overall contact with itsassociated vise jaw when the cylinder means is de-activated and beingurged to a pressure position by the activating forces, 7 a. said linkagemeans pushing at least a portion of the pressure plate means out ofcontact with its associated vise jaw when the piston is pushed to itssaid second position,

2. the pressure. plate means moving outwardly from the adjustable jaw ina pivotal movement.

4. The invention of claim 3 wherein the said power cam and jaw cam havecombined leverage'about their respective pivotal connections when urgedto the said pressure position to increase the pressures exerted by thepiston rod.

5. The invention of claim 4 wherein the pressures exerted by the pistonrod are-increased substantially by the linkage means. I

6. The invention of claim 5 wherein the pressures are increased by aratio of at least eight to one.

7. In an automatic operating vise of the type incorporating a fixed jawand an adjustable jaw movable with respect to the fixed jaw to secure, awork tween, the combinationof A. cylinder means provided in theadjustable jaw,

1. said cylinder means having; a piston reciprocal therein, v

2. said cylinder means receiving activating forces to push the pistonfrom a first position to a second position within the cylinder means,

a. said piston moving a piston rod within the said jaw in response tothe activating forces,

b.. said cylinder means including means to return the piston to its saidfirst position upon removal of the activating forces;

B. linkage means in contact with the said piston rod,

1. said linkage means having an initial position when the said cylinderis de-activated and having a pressure position when the activatingforces push the piston to its said second position,

2. the linkage means comprising a jaw cam pivotally connected to theadjustable jaw, wherein the I jaw cam has a crank arm and wherein thepiston rod contacts a portion of the jaw cam to rotate the jaw cam aboutits pivotal connections, the

piece therebea crank arm functioning to push a portion of the pressureplate means out of contact with the adjustable jaw when the linkagemeans are urged to the said pressure position;

C. pressure plate means connected to the adjustable vise jaw,

1. said pressure plate means having an initial position in overallcontact with its associated vise jaw when the cylinder means arede-activated and being urged to a pressure position by the activatingforces,

a. said linkage means pushing at least a portion of the pressure platemeansout of contact with its associated vise jaw when the piston ispushed to its said second position.

8. In an automatic operating vise of the type incorporating a fixed jawand an adjustable jaw movable with respect to the fixed jaw to secure awork piece therebetween, the combination of A. cylinder means providedin the adjustable jaw,

l. said cylinder means having a piston reciprocal therein,

2. said cylinder means receiving activating forces to push the pistonfrom a first position to a second position within the cylinder means,

a. said piston moving a piston rod within the said jaw in response tothe activating forces,

b. said cylinder means including means to return the piston to its saidfirst position upon removal of the activating forces;

2. the linkage meansincluding upper and lower pressure plate operatinglinkage rearwardly pivotally connected to the adjustable vise jaw andforwardly pivotally connected to the pressure plate means, the saidpiston rod terminating forwardly in angular cam operators which contactportions of the upper and lower pressure plate operating linkage whenthe piston is pushed to its second position to urge the pressure platemeans to its said pressure position; C. pressure plate means connectedto the adjustable vise jaw,

1. said pressure plate means having an initial position in overallcontact with its associated vise jaw when the cylinder means arede-activated and being urged to a pressure position by the activatingforces,

a. said linkage means pushing at least a portion of the pressure platemeans out of contact with its associated vise jaw when the piston ispushed to its said second position. I

9. The invention of claim 8 wherein the pressur plate means moveoutwardly from the adjustable jaw in continuous vertical alignment.

1. In an automatic operating vise of the type incorporating a fixed jawand an adjustable jaw movable with respect to the fixed jaw to secure awork piece therebetween, the combination of A. cylinder means providedin one said jaw,
 1. said cylinder means having a piston reciprocaltherein,
 2. said cylinder means receiving activating forces to push thepiston from a first position to a second position within the cylindermeans, a. said piston moving a piston rod within the said jaw inresponse to the activating forces, b. said cylinder means includingmeans to return the piston to its said first position upon removal ofthe activating forces; B. linkage means in contact with the said pistonrod,
 1. said linkage means having an initial position when the saidcylinder is de-activated and having a pressure position when theactivating forces push the piston to its said second position; and C.pressure plate means connected to one said vise jaw,
 1. said pressureplate means having an initial position in overall contact with itsassociated vise jaw when the cylinder means is de-activated and beingurged to a pressure position by the activating forces, a. said linkagemeans pushing at least a portion of the pressure plate means out ofcontact with its associated vise jaw when the piston is pushed to itssaid second position,
 2. the said pressure plate means being connectedto the one said vise jaw by means of ball and socket junctions.
 2. thelinkage means including upper and lower pressure plate operating linkagerearwardly pivotally connected to the adjustable vise jaw and forwardlypivotally connected to the pressure plate means, the said piston rodterminating forwardly in angular cam operators which contact portions ofthe upper and lower pressure plate operating linkage when the piston ispushed to its second position to urge the pressure plate means to itssaid pressure position; C. pressure plate means connected to theadjustable vise jaw,
 2. said cylinder means receiving activating forcesto push the piston from a first position to a second position within thecylinder means, a. said piston moving a piston rod within the said jawin response to the activating forces, b. said cylinder means includingmeans to return the piston to its said first position upon removal ofthe activating forces; B. linkage means in contact with the said pistonrod,
 2. the linkage means comprising a jaw cam pivotally connected tothe adjustable jaw, wherein the jaw cam has a crank arm and wherein thepiston rod contacts a portion of the jaw cam to rotate the jaw cam aboutits pivotal connections, the crank arm functioning to push a portion ofthe pressure plate means out of contact with the adjustable jaw when thelinkage means are urged to the said pressure position; C. pressure platemeans connected to the adjustable vise jaw,
 2. said cylinder meansreceiving activating forces to push the piston from a first position toa second position within the cylinder means, a. said piston moving apiston rod within the said jaw in response to the activating forces, b.said cylinder means including means to return the piston to its saidfirst position upon removal of the activating forces; B. linkage meansin contact with the said piston rod,
 2. the pressure plate means movingoutwardly from the adjustable jaw in a pivotal movement.
 2. said linkagemeans comprising a power cam and a jaw cam pivotally connected to theadjustable jaw, a. the said piston rod pivoting the power cam uponfunction of the cylinder means and the said power cam pivoting the jawcam to urge the pressure plate means outwardly from the adjustable jaw;and C. pressure plate means connected to one said vise jaw,
 2. saidcylinder means receiving activating forces to push the piston from afirst position to a second position within the cylinder means, a. saidpiston moving a piston rod within the said jaw in response to theactivating forces, b. said cylinder means including means to return thepiston to its said first position upon removal of the activating forces,2. The invention of claim 1 wherein the ball and socket junctions permitpivotal movement of the pressure plate means with regard to theassociated vise jaw.
 2. the said pressure plate means being connected tothe one said vise jaw by means of ball and socket junctions.
 2. saidcylinder means receiving activating forces to push the piston from afirst position to a second position within the cylinder means, a. saidpiston moving a piston rod within the said jaw in response to theactivating forces, b. said cylinder means including means to return thepiston to its said first position upon removal of the activating forces;B. linkage means in contact with the said piston rod,
 3. In an automaticvise of the type incorporating a fixed jaw and an adjustable jaw movablewith respect to the fixed jaw to secure a workpiece therebetween, thecombination of A. cylinder means provided in one said jaw,
 3. the onesaid jaw being the adjustable jaw; B. linkage means in contact with thesaid piston rod,
 4. The invention of claim 3 wherein the said power camand jaw cam have combined leverage about their respective pivotalconnections when urged to the said pressure position to increase thepressures exerted by the piston rod.
 5. The invention of claim 4 whereinthe pressures exerted by the piston rod are increased substantially bythe linkage means.
 6. The invention of claim 5 wherein the pressures areincreased by a ratio of at least eight to one.
 7. In an automaticoperating vise of the type incorporating a fixed jaw and an adjustablejaw movable with respect to the fixed jaw to secure a work piecetherebetween, the combination of A. cylinder means provided in theadjustable jaw,
 8. In an automatic operating vise of the typeincorporating a fixed jaw and an adjustable jaw movable with respect tothe fixed jaw to secure a work piece therebetween, the combination of A.cylinder means provided in the adjustable jaw,
 9. The invention of claim8 wherein the pressure plate means move outwardly from the adjustablejaw in continuous vertical alignment.